CN116498558A - Screw compressor - Google Patents

Abstract

The application discloses a screw compressor, include: a housing, a rotor set, an exhaust passage, and at least one muffler set. The muffler assembly is disposed in the exhaust passageway to eliminate noise in the exhaust passageway, the muffler assembly including a front end plate, a rear end plate, and a plurality of dividing plates, each dividing plate dividing a space between the front end plate and the rear end plate into a plurality of muffler chambers, each muffler chamber having a muffler inlet and a muffler outlet, each muffler inlet being in fluid communication with the rotor outlet independently, each muffler outlet being in fluid communication with the exhaust outlet independently. In the screw compressor of the application, the muffler groups with the muffler cavities of a plurality of expansion mufflers arranged side by side to form are arranged in the exhaust channel, so that the space of the exhaust channel is fully utilized, the upper limit of plane waves is improved, the upper limit of effective muffling frequency is higher, and more noise can be eliminated.

Description

Screw compressor

Technical Field

The present application relates to the field of compressors, and in particular to a screw compressor.

Background

The screw compressor comprises a pair of rotors, and the suction, compression and discharge processes of gas are completed by utilizing the mutual meshing of rotor teeth of the pair of rotors to cause the change of the volume of a primitive consisting of tooth-shaped spaces. The screw compressor forms discontinuous inter-tooth volumes through the meshing of the rotors, so that the suction cavity and the exhaust cavity are periodically communicated with the working cavity, unstable flow of gas is caused, pressure pulsation in suction and exhaust processes is caused, and vibration and noise of the compressor are caused.

Disclosure of Invention

At least one object of the present application is to provide a screw compressor comprising: a housing, a rotor set, an exhaust passage, and at least one muffler set. The housing has an air intake and an air exhaust. The rotor set is housed in the housing and rotates in an axial direction, the rotor set having a rotor inlet and a rotor outlet, the rotor set being configured to discharge gas sucked from the rotor inlet after compression from the rotor outlet, wherein the rotor inlet is in fluid communication with the suction port and the rotor outlet is in fluid communication with the exhaust port. The exhaust passage fluidly communicates the rotor outlet with the exhaust port such that compressed gas discharged from the rotor outlet is discharged from the exhaust port through the exhaust passage. The muffler group is arranged in the exhaust passage to eliminate noise in the exhaust passage, the muffler group comprises a front end plate, a rear end plate and a plurality of partition plates, the front end plate and the rear end plate are oppositely arranged along the axial direction of the rotor group at intervals, each partition plate is connected between the front end plate and the rear end plate to divide the space between the front end plate and the rear end plate into a plurality of muffler cavities, each muffler cavity is provided with a muffler inlet and a muffler outlet, each muffler inlet is independently in fluid communication with the rotor outlet, and each muffler outlet is independently in fluid communication with the exhaust port. Wherein the muffler inlet is provided on the front end plate, the muffler outlet is provided on the rear end plate, and the sectional areas of the muffler inlet and the muffler outlet are smaller than the sectional area of the sound-deadening chamber.

According to the above, the several sound damping chambers in each of the sound damping groups are arranged side by side around the axial direction of the rotor group.

According to the above, the exhaust passage is defined by a chamber wall to which the front end plate and the rear end plate of the muffler group are connected. Wherein the cavity wall encloses the sound damping cavity around the axial direction of the rotor set.

In accordance with the foregoing, the muffler assembly includes a sealing plate that is connected to the front end plate and the rear end plate, and that encloses the muffling cavity around the axis of the rotor assembly.

According to the above, the screw compressor further includes a barrel portion connected between the front end plate and the rear end plate, the barrel portion defining a connection passage that directly fluidly communicates the rotor outlet with the exhaust port, and the connection passage extends in an axial direction of the rotor group, wherein the plurality of sound-deadening chambers are provided outside the barrel portion around the connection passage.

According to the above, the exhaust port can cover the connection passage and the muffler outlet in the axial section.

According to the above, the housing includes an exhaust outer housing and an exhaust inner housing provided in the exhaust outer housing, the exhaust passage being defined in common between the exhaust outer housing and the exhaust inner housing and inside the exhaust inner housing, the exhaust passage including an annular passage surrounding the exhaust inner housing. The exhaust inner shell is provided with an inner shell air outlet, and the inner shell air outlet is in fluid communication with the muffler inlet of the muffler group through the annular channel.

According to the above, the front end plate and the rear end plate are arranged in parallel.

According to the above, the front end plate and the rear end plate are not disposed in parallel so that at least a part of the plurality of sound-deadening chambers have different lengths in the axial direction of the rotor group.

According to the above, the front end plate and the rear end plate are disposed perpendicular to the axial direction of the rotor set.

According to the above, at least a part of the muffler inlets in the muffler group are formed by openings in the front end plate.

According to the above, the at least one muffler group includes a plurality of muffler groups, which are arranged in the axial direction of the rotor group, and the muffler inlets and muffler outlets of adjacent muffler groups are disposed in alignment.

According to the above, the muffler group is configured to set the muffling frequency and the muffling amount that cancel noise in the exhaust passage by the number of the muffling chambers, the length of the muffling chambers in the axial direction of the rotor group, the sectional area ratio of the muffler inlet to the muffling chamber, and the sectional area ratio of the muffler outlet to the muffling chamber.

Other features, advantages, and embodiments of the application may be set forth or apparent from consideration of the following detailed description, drawings, and claims. Furthermore, it is to be understood that both the foregoing summary and the following detailed description are exemplary and intended to provide further explanation without limiting the scope of the application as claimed. However, the detailed description and specific examples merely indicate preferred embodiments of the present application. Various changes and modifications within the spirit and scope of the present application will become apparent to those skilled in the art from this detailed description.

Drawings

FIG. 1A is a perspective block diagram of a screw compressor according to one embodiment of the present application;

FIG. 1B is a top view of the screw compressor of FIG. 1A;

FIG. 2A is an exploded view of the screw compressor of FIG. 1A;

FIG. 2B is a cross-sectional view of the screw compressor of FIG. 1B taken along line A-A;

FIG. 2C is a cross-sectional view of the screw compressor of FIG. 1B taken along line B-B;

FIG. 2D is a cross-sectional view of the screw compressor of FIG. 1B taken along line C-C;

FIG. 3A is a perspective view of another embodiment of the exhaust housing of FIG. 1A;

FIG. 3B is an exploded view of the exhaust housing shown in FIG. 3A;

FIG. 3C is a cross-sectional view of the exhaust housing shown in FIG. 3A;

FIG. 3D is another cross-sectional view of the exhaust housing shown in FIG. 3A;

FIG. 4A is an exploded view of yet another embodiment of the exhaust housing of FIG. 1A;

FIG. 4B is a cross-sectional view of the exhaust housing shown in FIG. 4A;

FIG. 4C is another cross-sectional view of the exhaust housing shown in FIG. 4A;

FIG. 5A is an exploded view of yet another embodiment of the exhaust housing of FIG. 1A;

FIG. 5B is a cross-sectional view of the exhaust housing shown in FIG. 5A;

FIG. 5C is another cross-sectional view of the exhaust housing shown in FIG. 5A;

FIG. 6 is a cross-sectional view of yet another embodiment of the exhaust housing of FIG. 1A;

FIG. 7A is a perspective view of still another embodiment of the muffler assembly of FIG. 1A;

FIG. 7B is a top view of the muffler assembly shown in FIG. 7A;

FIG. 8A is a perspective view of still another embodiment of the exhaust housing of FIG. 1A;

FIG. 8B is an exploded view of the exhaust housing of FIG. 8A;

FIG. 9A is a graph of the muffling frequencies of one of the muffling chambers of FIG. 2A versus a muffling chamber including an inlet conduit and an outlet conduit;

fig. 9B is a graph comparing the muffling frequencies of the plurality of muffling chambers of fig. 2A with an overall muffling chamber that does not include a separate plate.

Detailed Description

Various embodiments of the present application are described below with reference to the accompanying drawings, which form a part hereof. It is to be understood that, although directional terms, such as "front", "rear", "upper", "lower", "left", "right", "top", "bottom", etc., may be used in this application to describe various example structural portions and elements of the present application, these terms are used herein for convenience of description only and are determined based on the example orientations shown in the drawings. Because the embodiments disclosed herein may be arranged in a number of different orientations, the directional terminology is used for purposes of illustration and is in no way limiting.

Fig. 1A and 1B show a structure of a screw compressor 100 according to an embodiment of the present application for explaining an external structure of the screw compressor 100. Fig. 1A is a perspective view of a screw compressor 100, and fig. 1B is a top view of fig. 1A. As shown in fig. 1A and 1B, the screw compressor 100 includes a housing 101, and the housing 101 has a substantially long cylindrical shape and includes a rotor housing 102 and a discharge housing 104 connected in sequence in the longitudinal direction. The rotor housing 102 has an air suction port 105, and the rotor housing 102 is mainly for accommodating the motor 212 and the rotor set 221 (see fig. 2B) for rotation therein. The exhaust housing 104 has an exhaust port 106, and the exhaust housing 104 is configured to exhaust the compressed gas from the exhaust port 106. Accordingly, the air flows substantially in the longitudinal direction after entering the housing 101 through the air inlet 105, is compressed, and is discharged from the housing 101 through the air outlet 106.

Fig. 2A to 2D show the internal structure of the screw compressor 100 shown in fig. 1A. Wherein fig. 2A shows an exploded view of screw compressor 100, fig. 2B shows a cross-sectional view of screw compressor 100 along line A-A, fig. 2C shows a cross-sectional view of screw compressor 100 along line B-B, and fig. 2D shows a cross-sectional view of screw compressor 100 along line C-C. As shown in fig. 2A to 2D, in the present embodiment, the screw compressor 100 is a twin screw compressor. The rotor set 221 includes a pair of rotors arranged in parallel side-by-side relationship, including a male rotor and a female rotor, as will be appreciated by those skilled in the art, only the male rotor is shown in the cut-away position as shown. The male rotor and the female rotor are engaged with each other, and the male rotor is connected to the motor 212 so that a pair of rotors can be driven to rotate individually by the motor 212. The pair of rotors have axes parallel to each other, and the male rotor and the female rotor rotate about the respective axes. In the present embodiment, the extending direction of the axis is the axial direction of the rotor group 221, the direction around the axial direction is the circumferential direction of the rotor group 221, and the direction perpendicular to the axial direction and the circumferential direction is the radial direction of the rotor group 221.

The male rotor and the female rotor are respectively provided with a plurality of spiral teeth, and grooves are formed between adjacent teeth at intervals. The male and female rotors are in meshed configuration with respective teeth and corresponding grooves and cooperate to define a plurality of spaced compression pockets 225 with the rotor housing 102. Rotor set 221 has a rotor inlet 222 and a rotor outlet 223. The rotor inlet 222 is located at the left end of the rotor set 221 and is in fluid communication with the suction port 105. Rotor outlet 223 is located at the right end of rotor set 221 and is in fluid communication with exhaust port 106. Each compression pocket 225 moves axially from rotor inlet 222 to rotor outlet 223 independently of the others. Gas is drawn into the compression pockets 225 from the rotor inlet 222 and as the rotor set 221 rotates, the compression pockets 225 gradually move toward the rotor outlet 223. At the same time, the volume of the compression chamber 225 is gradually reduced as the rotor set 221 rotates, and the gas in the compression chamber 225 is gradually compressed. The compressed gas exits rotor outlet 223.

The exhaust housing 104 has an exhaust passage 217 therein. Exhaust port 106 is located in the middle of exhaust housing 104 and rotor outlet 223 is in fluid communication with exhaust port 106 through exhaust passage 217 such that compressed gas discharged from rotor outlet 223 is discharged from exhaust port 106 through exhaust passage 217.

When the screw compressor 100 is operated, the engagement of the pair of rotors of the rotor set 221 forms a discontinuous compression pocket 225 such that compressed gas is intermittently discharged from the rotor outlet 223 and then flows through the discharge passage 217 and then is discharged from the discharge port 106, thereby generating discharge pressure pulsations of high acoustic energy, causing vibration and noise of the screw compressor 100.

In order to reduce the noise effect of the exhaust pressure pulsations, the screw compressor 100 further comprises at least one muffler set 240, the muffler set 240 being arranged in the exhaust channel 217 for eliminating noise in the exhaust channel 217. In the present embodiment, the at least one muffler group 240 includes one muffler group. It will be appreciated by those skilled in the art that depending on the size of the space of the exhaust passage 217 and the size of the muffler groups 240, at least one of the muffler groups 240 may also include more muffler groups that may be connected in series or parallel in the exhaust passage 217.

Specifically, each muffler group 240 includes a front end plate 241, a rear end plate 242, and a plurality of partition plates 243. The front end plate 241 and the rear end plate 242 are disposed opposite to and spaced apart from each other in the axial direction of the rotor set 221, and a partition plate 243 is connected between the front end plate 241 and the rear end plate 242 to partition the space between the front end plate 241 and the rear end plate 242 into a plurality of sound-deadening chambers 248. In this embodiment, the muffler assembly 240 further includes a sealing plate 249, the sealing plate 249 being connected to the outer edges of the front end plate 241 and the rear end plate 242 such that the sealing plate 249 encloses each of the sound attenuation cavities 248 about the axial direction of the rotor assembly 221. That is, the sealing plate 249, the front end plate 241, and the rear end plate 242 collectively define a closed sound damping space, and the partition plate 243 partitions the closed sound damping space into a plurality of sound damping chambers 248. And in the present embodiment, the front end plate 241 and the rear end plate 242 are disposed substantially parallel perpendicularly to the axial direction, and the partition plate 243 is connected between the front end plate 241 and the rear end plate 242 in the radial direction.

Each of the sound-deadening chambers 248 has a muffler inlet 245 and a muffler outlet 246, the muffler inlet 245 being provided on the front end plate 241, and the muffler outlet 246 being provided on the rear end plate 242. The muffler inlet 245 of each muffler chamber 248 is in fluid communication with the rotor outlet 223 independently of each other, and the muffler outlet 246 of each muffler chamber 248 is in fluid communication with the exhaust port 106 independently of each other. That is, compressed gas discharged from the rotor outlet 223 enters the muffler chambers 248 through the respective muffler inlets 245, and is discharged from the corresponding muffler outlets 246, and is further discharged from the exhaust port 106. The cross-sectional area of the muffler inlet 245 and muffler outlet 246 is smaller than the cross-sectional area of the muffling cavity 248. Because of this change in cross-sectional area, the muffler set 240 can form an expanding muffler set, and the sound wave energy is dissipated as the compressed gas enters the sound damping chamber 248 through the muffler inlet 245 and exits the muffler outlet 246, so that the muffler set 240 can dampen noise. The cross-sectional area here refers to the cross-sectional area on the axis section at the muffler inlet and the muffler outlet as shown in fig. 2D.

In the present embodiment, the exhaust casing 104 of the casing 101 includes an exhaust outer casing 214 and an exhaust inner casing 213, and the exhaust inner casing 213 is provided inside the exhaust outer casing 214. An inner passage 219 is defined in exhaust inner housing 213 in fluid communication with rotor outlet 223, and inner passage 219 and exhaust outer housing 214 and exhaust inner housing 213 cooperate to define an exhaust passage 217 therebetween. In the present embodiment, the muffler group 240 is provided at the end in the axial direction of the exhaust inner housing 213, the front end plate 241 of the muffler group 240 abuts against the end of the exhaust inner housing 213, and the seal plate 249 of the muffler group 240 is connected with the inner wall of the exhaust outer housing 214 to fix the position of the muffler group 240 in the exhaust housing 104. As one example, the closure plate 249 is welded to the exhaust outer housing 214. The exhaust passage 217 includes an annular passage 218 defined collectively by the exhaust inner housing 213, the exhaust outer housing 214, and the front end plate 241 of the muffler assembly 240, the annular passage 218 being disposed around the exhaust inner housing 213. And each muffler inlet 245 on the front end plate 241 is in fluid communication with the annular channel 218. The inner passage 219 forms an inner housing air outlet 215 on the exhaust inner housing 213, the inner housing air outlet 215 being in fluid communication with the annular passage 218. Accordingly, the compressed gas discharged from the rotor outlet 223 is discharged from the inner housing gas outlet 215 into the annular passage 218 through the inner passage 219 after entering the exhaust housing 104, then enters the muffler group 240 through the muffler inlet 245, is discharged from the muffler outlet 246 after being muffled by the muffler group 240, and finally is discharged from the exhaust port 106.

As a specific example, to mate with the annular channel 218, the muffler assembly 240 further includes a shroud 247 disposed inside the shroud 249. The shroud 247 is radially opposed to and spaced apart from the seal plate 249. A plurality of partition plates 243 are radially connected between the closing plate 249 and the surrounding plate 247 to define a plurality of sound-deadening chambers 248 arranged side by side around the axial direction, and a hollow portion 244 is formed between these sound-deadening chambers 248. In the axial cross section of the muffler assembly 240, the hollow 244 is substantially the same size as the end of the exhaust inner housing 213, and the side-by-side muffler chambers 248 have a size that substantially matches the annular passage 218, which will reduce the pressure loss of the compressed gas from the annular passage 218 into and out of the muffler assembly 240. As a more specific example, the hollow 244 extends from the middle to the bottom, that is, the sound-damping chambers 248 disposed side by side in the circumferential direction are not disposed as a complete revolution. Each muffler inlet 245 and muffler outlet 246 are disposed at a lower corner of the respective muffler chamber 248, such as a corner formed by the partition plate 243 and the sealing plate 249, or a corner formed by the partition plate 243 and the sealing plate 247, respectively. This facilitates the discharge of droplets of lubricating oil and the like entrained in the compressed gas from muffler outlet 246 as the compressed gas enters muffler chamber 248.

In the illustrated embodiment, the inner housing air outlet 215 includes a pair of inner housing air outlets 215a and 215b. The inner passage 219 extends generally axially in the exhaust inner housing 213 and then radially to both sides of the exhaust inner housing 213 to form inner housing air outlets 215a and 215b on both sides of the exhaust inner housing 213. This arrangement enables the inner housing air outlets 215a and 215b to be in fluid communication with the annular passage 218 from both sides even if the muffler group 240 abuts against the front end in the axial direction of the exhaust inner housing 213.

It will be appreciated by those skilled in the art that while a sealing plate 249 is included in the present embodiment, in other embodiments, a sealing plate may not be included and the front and rear end plates 241, 242 may be directly connected to the inner wall of the exhaust housing 104 to define a closed sound damping space.

Thus, the screw compressor 100 is able to flow through the muffler set 240 after the compressed gas enters the exhaust passage 217 to eliminate noise in the exhaust passage 217. Acoustic waves are utilized to reflect at the variations in cross-sectional areas of the muffler inlet 245, muffling chamber 248, and muffler outlet 246 to reduce acoustic wave energy and thereby reduce noise.

The muffler group 240 sets the muffling frequency and the muffling amount that cancel noise in the exhaust passage 217 by setting the number of muffling chambers 248, the length of the muffling chambers 248 in the axial direction, the ratio of the sectional areas of the muffler inlet 245 and the muffling chambers 248, and the ratio of the sectional areas of the muffler outlet 246 and the muffling chambers 248.

Specifically, the primary cancellation frequency of the muffling chamber 248 is mainly determined by the length of the muffling chamber 248 in the axial direction, and the shorter the length, the higher the primary cancellation frequency. In the present embodiment, since the front end plate 241 is disposed in parallel with the rear end plate 242, the main extinction frequency of each of the extinction chambers 248 is substantially the same. In some other embodiments, the front end plate 241 and the rear end plate 242 may be disposed non-parallel such that each of the sound attenuation chambers 248 has a different primary frequency of attenuation. Under the condition that the front end plate and the rear end plate are not parallel, the axial length of one sound-absorbing cavity is estimated initially through the axle center distance of the two end plates, then the initial area ratio is calculated based on the projection area of the inlet and the outlet of the sound-absorbing cavity on the cross section, then a transmission loss curve (Transmission Loss curve) is simulated, and finally the final size parameter of the sound-absorbing cavity is determined.

The upper frequency of effective muffling of muffling cavities 248 is primarily determined by the number of muffling cavities 248. The greater the number of sound attenuation chambers 248 in the same size space, the higher the upper frequency of effective sound attenuation.

The amount of damping of the damping chamber 248 is primarily determined by the ratio of the cross-sectional areas of the muffler inlet 245 and the damping chamber 248, and the ratio of the cross-sectional areas of the muffler outlet 246 and the damping chamber 248 (i.e., the expansion ratio). The larger the expansion ratio, the larger the sound-deadening amount.

Fig. 3A-3D illustrate another embodiment of an exhaust housing 304, wherein fig. 3A is a perspective view of the exhaust housing 304, fig. 3B is an exploded view of fig. 3A, fig. 3C is a cross-sectional view of the exhaust housing 304 along line D-D, and fig. 3D is a cross-sectional view of the exhaust housing 304 along line E-E. As shown in fig. 3A-3D, in this embodiment, exhaust housing 304 no longer includes an exhaust inner housing, but rather an axially extending exhaust passage 317 is formed directly in exhaust housing 304, exhaust passage 317 being defined by plenum wall 316 of exhaust housing 304 such that exhaust passage 317 is in fluid communication with rotor outlet 223 and exhaust port 306.

The structure of the muffler set 340 is also different from that of the muffler set 240. Specifically, the muffler group 340 does not include a sealing plate, and the front end plate 341 and the rear end plate 342 thereof are shaped to match the shape of the inner surface of the cavity wall 316 so that the front end plate 341 and the rear end plate 342 can be directly connected to the cavity wall 316, thereby forming a closed sound deadening space between the front end plate 341, the rear end plate 342, and the cavity wall 316. A partition plate 343 is radially connected between the front end plate 341 and the rear end plate 342 to partition the closed sound deadening space into several sound deadening chambers 348. Each muffler chamber 348 has muffler inlet 345 and muffler outlet 346 disposed on the front and rear end plates 341, 342, respectively. In this embodiment, the edges of the front end plate 441, the rear end plate 442, and the divider plate 443 are connected to the chamber wall 416, for example, by welding, interference fit, or integral casting.

In the present embodiment, the muffler group 340 further includes a cylindrical portion 352, and the cylindrical portion 352 is connected between the front end plate 341 and the rear end plate 342. An axially extending connecting passage 358 is defined in the barrel portion 352, the connecting passage 358 extending through the front and rear end plates 341, 342 to directly fluidly communicate the rotor outlet 223 and the exhaust ports 306. In the present embodiment, the tube portion 352 is connected at the middle of the front end plate 341 and the rear end plate 342, and the partition plate 343 is radially connected between the tube portion 352 and the chamber wall 316, so that the plurality of sound-deadening chambers 348 are arranged side by side outside the tube portion 352 around the connection passage 358. By providing the tube portion 352 and the connection passage 358, most of the compressed gas can be discharged through the connection passage 358 without passing through the muffler group 340, and thus the muffler group 340 has little influence on the pressure loss of the compressed gas. In the present embodiment, the muffler inlets 345 and muffler outlets 346 of the plurality of muffler chambers 348 are provided on the front end plate 341 and the rear end plate 342 near the cylindrical portion 352, and are uniformly disposed circumferentially around the cylindrical portion 352. In the axial cross-section of the exhaust housing 304, the exhaust port 306 can cover the connection passage 358 and the muffler outlet 346 such that the compressed gas can be directly exhausted from the exhaust port 306 after flowing through the connection passage 358 or the muffler group 340. This can further reduce the pressure loss of the compressed gas. The cross-sectional areas of the muffler inlet 345 and the muffler outlet 346 are smaller than the cross-sectional area of the muffling cavity 348 so that the sound wave energy is consumed when the compressed gas enters the muffling cavity 348 through the muffler inlet 345 and is discharged from the muffler outlet 346, and thus the muffler assembly 340 can attenuate noise.

Fig. 4A-4C illustrate another embodiment of an exhaust housing 404, where fig. 4A is an exploded view of the exhaust housing 404, fig. 4B is a cross-sectional view of the exhaust housing 404 along line F-F, and fig. 4C is a cross-sectional view of the exhaust housing 404 along line G-G. As shown in fig. 4A-4C, exhaust housing 404 differs from exhaust housing 304 in that the structure of muffler set 440 is different from the structure of muffler set 340. Specifically, the muffler group 440 also includes a front end plate 441 and a rear end plate 442 disposed substantially in parallel, and a muffler inlet 445 and a muffler outlet 446 disposed on the front end plate 441 and the rear end plate 442, respectively, the muffler inlet 445 and the muffler outlet 446 being disposed correspondingly to reduce the pressure loss of the compressed gas. In this embodiment, however, the divider plates 443 of the muffler assembly 440 are no longer radially disposed, but are instead disposed in a "well" configuration to define a square-shaped muffler chamber 448. The edges of the front end plate 441, the rear end plate 442 and the dividing plate 443 are connected to the chamber wall 416, for example welded connections. The cross-sectional areas of muffler inlet 445 and muffler outlet 446 are smaller than the cross-sectional area of muffler chamber 448 such that the sound wave energy is dissipated as the compressed gas enters muffler chamber 448 through muffler inlet 445 and exits muffler outlet 346, so that muffler assembly 440 is able to attenuate noise.

Fig. 5A-5C illustrate yet another embodiment of an exhaust enclosure 504, where fig. 5A is an exploded view of the exhaust enclosure 504, fig. 5B is a cross-sectional view of the exhaust enclosure 504 at the D-D line in fig. 3B, and fig. 5C is a cross-sectional view of the exhaust enclosure 504 at the E-E line in fig. 3B. As shown in fig. 5A-5C, exhaust housing 504 differs from exhaust housing 304 in that the structure of muffler set 540 differs from the structure of muffler set 340. Specifically, the muffler group 540 also includes a front end plate 541 and a rear end plate 542 disposed substantially in parallel, and a muffler inlet 545 and a muffler outlet 546 disposed on the front end plate 541 and the rear end plate 542, respectively, the muffler inlet 545 and the muffler outlet 546 being disposed correspondingly to reduce the pressure loss of the compressed gas. In the present embodiment, however, the cylindrical portion 552 no longer penetrates the front and rear end plates 541, 542, but is connected between the front and rear end plates 541, 542 to form a cylindrical sound damping chamber 558 in the cylindrical portion 552. And the partition plate 543 is radially connected between the tube portion 552 and the chamber wall 516 such that a plurality of sound-deadening chambers 548 are arranged side by side outside the tube portion 552 around the sound-deadening chamber 558. The edges of the front end plate 541, the rear end plate 542, and the separation plate 543 are connected to the chamber wall 516, for example, welded connection. The cross-sectional areas of muffler inlet 545 and muffler outlet 546 are smaller than the cross-sectional areas of muffler chamber 548 and 558 such that when compressed gas enters muffler chamber 548 or 558 through muffler inlet 545 and exits muffler outlet 546, the acoustic energy is dissipated, and muffler assembly 540 is able to attenuate noise.

Fig. 6 illustrates yet another embodiment of the exhaust housing 604, wherein fig. 6 illustrates a cross-sectional view of the exhaust housing 604 at the location of line E-E in fig. 3B. As shown in fig. 6, the structure of the exhaust housing 604 is substantially the same as that of the exhaust housing 404, except that two muffler groups 640a and 640b having the same structure are provided in the exhaust housing 604 in the present embodiment. The muffler groups 640a and 640b are each identical in structure to the muffler group 440, except that the length of the sound-deadening chamber in the axial direction is different. The front end plate 641a and the rear end plate 642a of the muffler group 640a and the front end plate 641b and the rear end plate 642b of the muffler group 640b are disposed substantially in parallel, and the muffler inlet 645a and the muffler outlet 646a of the muffler group 640a and the muffler inlet 645b and the muffler outlet 646b of the muffler group 640b are disposed correspondingly to reduce the pressure loss of the compressed gas. And the sectional areas of the respective muffler inlets and muffler outlets are smaller than the sectional area of the muffling chamber so that the compressed gas discharged from the rotor outlet 223 can flow through the muffler group 640a and the muffler group 640b in order so that the sound wave energy is consumed, and thus the muffler group 540 can absorb noise.

Fig. 7A and 7B illustrate yet another embodiment of a muffler assembly 740. Fig. 7A is a perspective view of the muffler assembly 740, and fig. 7B is a top view of the muffler assembly 740. As shown in fig. 7A and 7B, in the present embodiment, the muffler group 740 also includes a front end plate 741 and a rear end plate 742, and a muffler inlet 745 and a muffler outlet 746 provided on the front end plate 741 and the rear end plate 742, respectively, the muffler inlet 745 and the muffler outlet 746 being provided correspondingly to reduce the pressure loss of the compressed gas. In the present embodiment, however, the front end plate 741 and the rear end plate 742 are not disposed in parallel any more, but are disposed in a fold line shape. The divider plates 743 of the muffler assembly 740 are arranged in a "well" to define a trapezoidal shaped muffling chamber 748. The cross-sectional areas of the muffler inlet 745 and the muffler outlet 746 are smaller than the cross-sectional area of the muffling cavity 748 such that the sound wave energy is consumed by the compressed gas as it enters the muffling cavity 748 through the muffler inlet 745 and exits the muffler outlet 746, and thus the muffler assembly 740 is able to attenuate noise.

Fig. 8A-8B illustrate a specific structure of yet another embodiment of an exhaust housing 804. Wherein fig. 8A shows a perspective view of the exhaust housing 804 and fig. 8B shows an exploded view of fig. 8A. As shown in fig. 8A and 8B, the structure of the exhaust housing 804 is substantially the same as that of the exhaust housing 104, except that the structure of the muffler group 840 is different from that of the muffler group 240, and the position of the exhaust port 806 is different from that of the exhaust port 106. Specifically, the muffler assembly 840 includes a front end plate 841, a rear end plate 842, a seal plate 849, and a shroud 847, the front end plate 841 and the rear end plate 842 being axially opposed and spaced apart, the shroud 847 and the seal plate 849 being radially opposed and spaced apart. And a shroud 847 and a seal plate 849 are connected between the front end plate 841 and the rear end plate 842, a plurality of partition plates (not shown in the figure, see partition plate 243 shown in fig. 2D) to form a plurality of sound-deadening chambers, and a hollow 844 is formed between these sound-deadening chambers. The muffler assembly 840 has the same muffler principles as the muffler assembly 240 and will not be described in detail herein. Unlike the muffler assembly 240, the rear end plate 842 no longer encloses the hollow 844, but only the individual sound-damping chambers. That is, the hollow 844 is in direct fluid communication with the exhaust ports 806. The provision of the rear end plate 842 in this way can reduce the amount of material used for the rear end plate 842, on the one hand, and the possibility of the rear end plate 842 vibrating and generating noise, on the other hand, as compared with the muffler assembly 240, because the gas in the exhaust passage hits the rear end plate 842.

Further referring to fig. 2D, after the compressed gas enters the muffler chambers, a part of the liquid can be discharged from the muffler outlets along with the gas flow, and another part of the liquid is deposited at the corners of the bottoms of the muffler chambers under the action of gravity, deposited to a certain amount, and then discharged from the muffler outlets. The liquid exiting the muffler outlet is discharged from the exhaust port 806 along with the flow of compressed gas.

In the present embodiment, the exhaust housing 804 also includes an exhaust outer housing 814 and an exhaust inner housing 813, and the exhaust port 806 is provided at the bottom of the end face of the exhaust outer housing 814. This arrangement can further facilitate timely discharge of droplets of lubricating oil and the like entrained in the compressed gas out of the exhaust housing 804.

Fig. 9A shows a graph of the sound damping performance of one sound damping chamber 248 of the muffler set of fig. 2A compared to a sound damping chamber including an inlet pipe and an outlet pipe, and fig. 9B shows a graph of the sound damping performance of a plurality of sound damping chambers 248 of fig. 2A compared to an overall sound damping chamber not including a partition plate, wherein the abscissa is the frequency of sound waves and the ordinate is the transmission loss of sound waves. Curve 981 shows the sound damping effect of a sound damping chamber comprising an inlet duct and an outlet duct, curve 982 shows the sound damping effect of a sound damping chamber 248 comprising only an opening-shaped sound damping inlet and outlet; curve 983 shows the sound damping effect of an overall sound damping chamber that does not include a divider plate, and curve 984 shows the sound damping effect of a plurality of sound damping chambers that include a divider plate.

As shown in fig. 9A, the muffler chamber 248, which includes only the muffler inlet and muffler outlet, has a smaller amount of muffling at certain frequencies than a muffler including the inlet pipe and the outlet pipe, but can also perform a certain muffling function. The amount of muffling at frequencies above 1400Hz is comparable to a muffler comprising an inlet pipe and an outlet pipe, while the amount of muffling in some frequency bands (900-1400 Hz) is even higher. And the muffler without the inlet pipeline and the outlet pipeline can greatly reduce the pressure loss of the compressed gas in the process of flowing through the muffler group. By providing a plurality of sound-deadening chambers 248 arranged side by side, the sound-deadening range can be increased, and the sound-deadening amount can be compensated.

As shown in fig. 9B, the upper limit frequency of effective sound elimination of the plurality of sound elimination chambers including the partition plate may reach about 2750Hz, whereas the sound elimination effect of the entire sound elimination chamber including no partition plate is not ideal at about 1700Hz or more. Therefore, the greater the number of sound deadening chambers provided in the same size space, the higher the upper limit frequency of effective sound deadening.

In the existing screw compressor, the compressed gas flowing through the discharge passage has discharge pressure pulsation of high acoustic energy, causing vibration and noise of the screw compressor. The exhaust channel has a limited size, in particular a limited length in the axial direction. The provision of a muffler in the exhaust passage is required to meet the dimensional requirements and to avoid excessive pressure loss of the muffler on the compressed gas.

In the screw compressor of the application, the muffler groups with the muffler cavities of a plurality of expansion mufflers arranged side by side to form are arranged in the exhaust channel, so that the space of the exhaust channel is fully utilized, the upper limit of plane waves is improved, the upper limit of effective muffling frequency is higher, and more noise can be eliminated.

And the muffler inlet and the muffler outlet of the muffler group of the present application are in an opening shape, excluding the inlet pipe and the outlet pipe, so that the muffler group does not cause excessive pressure loss to the compressed gas.

In addition, through setting up the sound attenuation chamber of different axial length, the noise elimination in the exhaust passage can also be eliminated to the silencer group of this application in wide frequency range.

While the present disclosure has been described in conjunction with the examples of embodiments outlined above, various alternatives, modifications, variations, improvements, and/or substantial equivalents, whether known or that are or may be presently or later be envisioned, may be apparent to those of ordinary skill in the art. Accordingly, the examples of embodiments of the disclosure as set forth above are intended to be illustrative, not limiting. Various changes may be made without departing from the spirit or scope of the disclosure. Accordingly, the present disclosure is intended to embrace all known or earlier developed alternatives, modifications, variations, improvements and/or substantial equivalents. The technical effects and problems of the present specification are illustrative and not restrictive. It should be noted that the embodiments described in the present specification may have other technical effects and may solve other technical problems.

Claims (13)

1. A screw compressor, comprising:

a housing having an air inlet and an air outlet;

a rotor set housed in the housing and rotating in an axial direction, the rotor set having a rotor inlet and a rotor outlet, the rotor set being configured to discharge gas sucked from the rotor inlet after compression from the rotor outlet, wherein the rotor inlet is in fluid communication with the suction port and the rotor outlet is in fluid communication with the exhaust port;

an exhaust passage fluidly connecting the rotor outlet with the exhaust port such that compressed gas exhausted from the rotor outlet is exhausted from the exhaust port through the exhaust passage; and

at least one muffler group disposed in the exhaust gas passage to eliminate noise in the exhaust gas passage, the muffler group including a front end plate, a rear end plate, and a plurality of partition plates disposed opposite and spaced apart in an axial direction of the rotor group, each partition plate being connected between the front end plate and the rear end plate to partition a space between the front end plate and the rear end plate into a plurality of muffler chambers, each muffler chamber having a muffler inlet and a muffler outlet, each muffler inlet being in fluid communication with the rotor outlet independently, each muffler outlet being in fluid communication with the exhaust gas outlet independently;

wherein the muffler inlet is provided on the front end plate, the muffler outlet is provided on the rear end plate, and the sectional areas of the muffler inlet and the muffler outlet are smaller than the sectional area of the sound-deadening chamber.

2. The screw compressor of claim 1, wherein:

the plurality of sound damping cavities in each of the sound damping groups are arranged side by side around the axial direction of the rotor group.

3. The screw compressor of claim 1, wherein:

the exhaust passage is defined by a cavity wall to which the front end plate and the rear end plate of the muffler group are connected;

wherein the cavity wall encloses the sound damping cavity around the axial direction of the rotor set.

4. The screw compressor of claim 1, wherein:

the muffler assembly includes a sealing plate connected to the front and rear end plates and enclosing the muffling cavity about an axial direction of the rotor assembly.

5. The screw compressor of claim 1, wherein:

the screw compressor further includes a barrel connected between the front and rear end plates, the barrel defining a connecting passage that directly fluidly communicates the rotor outlet with the exhaust port, and that extends in an axial direction of the rotor set, wherein the plurality of sound damping cavities are disposed outside the barrel about the connecting passage.

6. The screw compressor of claim 5, wherein:

the exhaust port can cover the connection passage and the muffler outlet in an axial section.

7. The screw compressor of claim 1, wherein:

the housing comprises an exhaust outer housing and an exhaust inner housing, the exhaust inner housing is arranged in the exhaust outer housing, the exhaust passage is jointly defined between the exhaust outer housing and the exhaust inner housing and inside the exhaust inner housing, and the exhaust passage comprises an annular passage surrounding the exhaust inner housing;

the exhaust inner shell is provided with an inner shell air outlet, and the inner shell air outlet is in fluid communication with the muffler inlet of the muffler group through the annular channel.

8. The screw compressor of claim 1, wherein:

the front end plate and the rear end plate are arranged in parallel.

9. The screw compressor of claim 1, wherein:

the front end plate and the rear end plate are not disposed in parallel such that at least a part of the plurality of sound-deadening chambers have different lengths in an axial direction of the rotor group.

10. The screw compressor of claim 1, wherein:

the front end plate and the rear end plate are disposed perpendicular to an axial direction of the rotor set.

11. The screw compressor of claim 1, wherein:

at least a portion of the muffler inlets in the muffler assembly are formed by openings in the front end plate.

12. The screw compressor of claim 1, wherein:

the at least one muffler group includes a plurality of muffler groups that are arranged in an axial direction of the rotor group, and the muffler inlets and muffler outlets of adjacent muffler groups are disposed in alignment.

13. The screw compressor of claim 1, wherein:

the muffler group is configured to set a muffling frequency and a muffling amount that cancel noise in the exhaust passage by the number of the muffling cavities, a length of the muffling cavities in an axial direction of the rotor group, a sectional area ratio of the muffler inlet to the muffling cavities, and a sectional area ratio of the muffler outlet to the muffling cavities.